JP2008524500A - Variable displacement vane pump with multiple control chambers - Google Patents

Variable displacement vane pump with multiple control chambers Download PDF

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JP2008524500A
JP2008524500A JP2007547124A JP2007547124A JP2008524500A JP 2008524500 A JP2008524500 A JP 2008524500A JP 2007547124 A JP2007547124 A JP 2007547124A JP 2007547124 A JP2007547124 A JP 2007547124A JP 2008524500 A JP2008524500 A JP 2008524500A
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pump
control
chamber
ring
control ring
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JP5116483B2 (en
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ウィリアムソン、マシュー
シャルバー、デイビッド、アール．
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マグナ パワートレイン インコーポレイテッド
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/04—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal axis type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

可変容量形ベーンポンプが提供される。ポンプはポンプ容量を変化させる可動式ポンプ制御リングを有し、ポンプは選択された少なくとも２つの平衡圧力のいずれか一方で作動することができる。ポンプリングは少なくとも第１および第２の制御チャンバによって可動され、制御チャンバは制御リングに当接して、それらチャンバに供給された加圧流体がポンプ制御リングに作用してポンプの容積を減少させるように、ポンプ制御リングを可動させる。加圧流体が一方の制御チャンバにのみ供給される場合には、ポンプは第１の平衡圧力で作動し、加圧流体が第２の制御チャンバにも供給される場合には、ポンプは第２の平衡圧力で作動する。所望であれば、加圧作動流体はまた第２の制御チャンバにのみ供給されてポンプを第３の平衡圧力で作動させることも可能でありかつ／または、必要であれば、追加的な制御チャンバを設けることもできる。  A variable displacement vane pump is provided. The pump has a movable pump control ring that varies the pump capacity, and the pump can operate at either of at least two selected equilibrium pressures. The pump ring is moved by at least the first and second control chambers such that the control chamber abuts the control rings so that pressurized fluid supplied to the chambers acts on the pump control ring to reduce the pump volume. Next, the pump control ring is moved. If pressurized fluid is supplied to only one control chamber, the pump operates at a first equilibrium pressure, and if pressurized fluid is also supplied to the second control chamber, the pump is second Operates at an equilibrium pressure of. If desired, pressurized working fluid can also be supplied only to the second control chamber to operate the pump at the third equilibrium pressure and / or, if necessary, an additional control chamber. Can also be provided.

Description

本発明は可変容量形ベーンポンプに関する。より詳細には、本発明は制御リングに隣接した２つまたはそれ以上の制御チャンバに作動流体を供給することによって少なくとも２つの異なった平衡圧力の間の選択が可能な可変容量形ベーンポンプに関する。   The present invention relates to a variable displacement vane pump. More particularly, the invention relates to a variable displacement vane pump that allows selection between at least two different equilibrium pressures by supplying working fluid to two or more control chambers adjacent to the control ring.

可変容量形ベーンポンプはよく知られており、ポンプのロータ偏心率を変え、それによってポンプ容積を変えるための可動式ポンプ制御リングの形の容量調節要素を含んでいてもよい。このポンプがほぼ一定のオリフィスサイズを有したシステム例えば自動車エンジン潤滑系に供給している場合には、ポンプ押出量の変化はポンプによって生み出される圧力の変化に等しい。   Variable displacement vane pumps are well known and may include a capacity adjusting element in the form of a movable pump control ring to change the rotor eccentricity of the pump and thereby change the pump volume. If the pump is feeding a system with a substantially constant orifice size, such as an automobile engine lubrication system, the change in pump output is equal to the change in pressure produced by the pump.

平衡圧力を維持するためにポンプの容積を変化させる機能を有することは、ポンプが作動速度の範囲全体にわたって作動させられる、例えば自動車潤滑ポンプのような環境において重要である。この種の環境において、平衡圧力を維持するために、ポンプ押出作動流体（例えば潤滑油）をポンプの出力からポンプ制御リングに隣接する制御チャンバにフィードバック供給し、制御チャンバ内の圧力を作用させて通例戻しばねの付勢力に抗して制御リングを可動させ、これにより、ポンプの容量を変化させる方式を採用することは公知である。   Having the ability to vary the volume of the pump to maintain the equilibrium pressure is important in environments such as automotive lubrication pumps where the pump is operated over the full range of operating speeds. In this type of environment, in order to maintain an equilibrium pressure, pump extrusion working fluid (eg, lubricating oil) is fed back from the pump output to the control chamber adjacent to the pump control ring to act on the pressure in the control chamber. It is known to employ a scheme in which the control ring is moved against the biasing force of the return spring, thereby changing the capacity of the pump.

ポンプ押出圧力が増大する場合、例えばポンプの作動速度が高まる場合には、高まった圧力が制御リングに作用し、戻しばねの付勢力に打ち勝ってポンプ容量を減少させるように制御リングを可動させ、これにより押出量が減少して、従ってポンプ押出圧力が減少する。   When the pump extrusion pressure increases, for example when the pump operating speed increases, the increased pressure acts on the control ring and moves the control ring to overcome the biasing force of the return spring and reduce the pump capacity, This reduces the amount of extrusion and hence the pump extrusion pressure.

逆に、例えばポンプの作動速度が低下する場合には、ポンプ押出圧力が低下するにつれて、制御リングに隣接した制御チャンバに与えられる圧力の低下は戻しばねの付勢が制御リングを可動させてポンプの容量を増大させるように作用し、これによりポンプの押出量が増大して、従ってポンプ圧力が増加する。このようにして、ポンプ出力で平衡圧力が確保される。   Conversely, for example, when the pump operating speed decreases, as the pump extrusion pressure decreases, the pressure applied to the control chamber adjacent to the control ring is reduced by the biasing of the return spring causing the control ring to move. Acts to increase the capacity of the pump, thereby increasing the pump output and thus the pump pressure. In this way, an equilibrium pressure is ensured with the pump output.

平衡圧力は、制御チャンバ内の作動流体が作用を及ぼす範囲の制御リング面積と、チャンバに供給される作動流体の圧力と、戻しばねによって生み出される付勢力とによって決定される。   The equilibrium pressure is determined by the control ring area to which the working fluid in the control chamber acts, the pressure of the working fluid supplied to the chamber, and the biasing force generated by the return spring.

従来、平衡圧力はエンジンの予測稼動範囲にとって許容可能な圧力であるように選択され、従って、例えばエンジンは低高稼動速度においてエンジン高稼動速度で要されるよりも低い作動流体圧力で無難に稼動し得ればよいことから、一定程度の妥協が許される。過度の損耗またはエンジンにとってその他の損傷を防止するため、エンジン設計者は最悪（高稼動速度）条件に対応するポンプ平衡圧力を選択するであろう。従って、低速時にポンプはそうした速度に必要とされるよりも高い容量で作動し、余分で不必要な作動流体をポンピングするエネルギーを浪費することになる。   Traditionally, the equilibrium pressure has been selected to be an acceptable pressure for the engine's expected operating range, so for example, the engine will operate safely at lower operating fluid pressures than required at higher engine operating speeds. Because it only has to be possible, a certain degree of compromise is allowed. In order to prevent excessive wear or other damage to the engine, the engine designer will select a pump equilibrium pressure that corresponds to the worst (high operating speed) conditions. Thus, at low speeds, the pump will operate at a higher capacity than required for such speeds, wasting energy to pump extra and unnecessary working fluid.

かなりコンパクトなポンプハウジングで、選択可能な少なくとも２つの平衡圧力を供することのできる可変容量形ベーンポンプを得ることが望ましい。また、ポンプ制御リング用の軸ピンに作用する反力が低下するような可変容量形ベーンポンプを得ることも望ましい。   It would be desirable to have a variable displacement vane pump capable of providing at least two selectable equilibrium pressures with a fairly compact pump housing. It is also desirable to obtain a variable displacement vane pump that reduces the reaction force acting on the shaft pin for the pump control ring.

本発明の目的は、従来の技術の少なくとも１つの短所を除去もしくは軽減する新規な可変容量形ベーンポンプを提供することである。   It is an object of the present invention to provide a novel variable displacement vane pump that eliminates or reduces at least one disadvantage of the prior art.

本発明の第１の態様によれば、ポンプ容量を変化させる可動式ポンプ制御リングを備え、選択された少なくとも２つの平衡圧力で作動可能な可変容量形ベーンポンプであって、吸込み口と吐出し口とを有するポンプチャンバを内蔵したポンプケーシングと、ポンプチャンバ内を可動してポンプの容量を変化させるポンプ制御リングと、ポンプ制御リング内に回転式に取り付けられたベーンポンプロータであって、ポンプ制御リングの内周面に接合するスライド式に取り付けられた複数枚の羽根を有し、ポンプ制御リングの中心から偏心した回転軸を有し、回転して、流体が吸込み口から吐出し口に向かって移動するにつれて流体を加圧するベーンポンプロータと、ポンプケーシングとポンプ制御リングとの間にある第１の制御チャンバであって、加圧流体を受け取って、ポンプの容積を減少させるためにポンプ制御リングを可動させる力を生み出すように作動する第１の制御チャンバと、ポンプケーシングとポンプ制御リングとの間にある第２の制御チャンバであって、加圧流体を受け取って、ポンプの容積を減少させるためにポンプ制御リングを可動させる力を生み出すように選択的に作動する第２の制御チャンバと、ポンプリングとケーシングとの間で作用して、最大容積が達成される位置に向かってポンプリングを付勢する戻しばねであって、第１と第２の制御チャンバの力に抗して作用して平衡圧力を達成する戻しばねとを備え、第２の制御チャンバに対する加圧流体の供給を実施もしくは排除させることによってポンプの平衡圧力が変化させられる、可変容量形ベーンポンプが提供される。   According to a first aspect of the present invention, there is provided a variable displacement vane pump having a movable pump control ring for changing a pump capacity and capable of operating at at least two selected equilibrium pressures, including a suction port and a discharge port. A pump casing having a built-in pump chamber, a pump control ring that moves inside the pump chamber to change the capacity of the pump, and a vane pump rotor that is rotatably mounted in the pump control ring, the pump control ring A plurality of blades attached in a sliding manner to be joined to the inner peripheral surface of the pump, having a rotating shaft that is eccentric from the center of the pump control ring, and rotating, fluid flows from the suction port toward the discharge port A vane pump rotor that pressurizes fluid as it moves, and a first control chamber between the pump casing and the pump control ring. A first control chamber operable to receive pressurized fluid and generate a force to move the pump control ring to reduce the volume of the pump; and a second between the pump casing and the pump control ring A second control chamber that selectively operates to receive a pressurized fluid and generate a force to move the pump control ring to reduce the volume of the pump; and a pump ring and a casing A return spring acting between and urging the pump ring toward a position where maximum volume is achieved, acting against the forces of the first and second control chambers to achieve an equilibrium pressure A variable displacement vane pump, comprising a return spring, wherein the equilibrium pressure of the pump can be varied by implementing or eliminating the supply of pressurized fluid to the second control chamber. Flops are provided.

本発明の第２の態様により、ポンプチャンバを内蔵したポンプケーシングと、ポンプチャンバ内に回転式に取り付けられたベーンポンプロータと、ベーンポンプロータにスライド式に取り付けられた複数の羽根と、ポンプチャンバ内でベーンポンプロータを包囲するポンプ制御リングであって、ベーンポンプロータはポンプ制御リングの中心から偏心した回転軸を有し、ポンプ制御リングは、ポンプの容量を変化させるために、ポンプチャンバ内で軸ピン周りに旋回運動可能なポンプ制御リングと、ポンプケーシング、ポンプ制御リング、軸ピン、およびポンプ制御リングとポンプケーシングとの間の弾性シールの間に形成された制御チャンバであって、加圧流体を受け取って、ポンプの容積を減少させるためにポンプ制御リングを可動させる力を生み出すように作動可能な制御チャンバと、ポンプリングとケーシングとの間で作用して、最大容積が達成される位置に向かってポンプリングを付勢する戻しばねであって、戻しばねは、制御チャンバの力に抗して作用して平衡圧力を達成し、軸ピンおよび弾性シールは制御チャンバ内に存在するポンプ制御リングの面積が減少するように配置され、制御チャンバ内の加圧流体によってポンプ制御リングに及ぼされる力を減少させ、可変容量形ベーンポンプが提供される。   According to a second aspect of the present invention, a pump casing incorporating a pump chamber, a vane pump rotor rotatably mounted in the pump chamber, a plurality of blades slidably mounted on the vane pump rotor, and a pump chamber A pump control ring that surrounds the vane pump rotor, the vane pump rotor having a rotational axis that is eccentric from the center of the pump control ring, the pump control ring being arranged around an axial pin in the pump chamber to change the pump capacity A control chamber formed between a pivotable pump control ring and a pump casing, a pump control ring, a shaft pin, and an elastic seal between the pump control ring and the pump casing for receiving pressurized fluid Move the pump control ring to reduce the pump volume A return spring acting between the pump ring and the casing that is operable to generate force and biasing the pump ring toward a position where maximum volume is achieved, the return spring comprising: Acting against the force of the control chamber to achieve the equilibrium pressure, the shaft pin and the elastic seal are arranged so that the area of the pump control ring present in the control chamber is reduced by the pressurized fluid in the control chamber A variable displacement vane pump is provided that reduces the force exerted on the pump control ring.

好ましくは、戻しばねは、ポンプ制御リングに加える付勢力が軸ピンに作用する反力をさらに減少させる方向を指向している。さらにまた好ましくは、制御チャンバは、軸ピンに対して、生ずる力が軸ピンに作用する反力を減少させるように配置されている。   Preferably, the return spring is directed in a direction in which a biasing force applied to the pump control ring further reduces a reaction force acting on the shaft pin. Still preferably, the control chamber is arranged with respect to the shaft pin so that the reaction force exerted on the shaft pin is reduced.

以下、例示のために添付図面を参照し、本発明の好ましい実施形態を説明する。   Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings for the purpose of illustration.

本発明の１実施形態による可変容量形ベーンポンプは、図１，２および３において一般に２０で表されている。   A variable displacement vane pump according to one embodiment of the present invention is generally designated 20 in FIGS.

図１，２および３において、ポンプ２０は、ポンプ２０が加圧作動流体を供給するエンジン（図示せず）等に対して、ポンプカバー（図示せず）および適切なガスケットによって封止された前面２４を有したハウジングないしケーシング２２を含んでいる。   1, 2, and 3, the pump 20 is a front face sealed by a pump cover (not shown) and appropriate gaskets, such as an engine (not shown) to which the pump 20 supplies pressurized working fluid. A housing or casing 22 with 24 is included.

ポンプ２０は、任意の適切な手段、例えばポンプが作動流体を供給するエンジンまたはその他の機構によって駆動されてポンプ２０を作動させる駆動軸２８を含んでいる。駆動軸２８が回転させられると、ポンプチャンバ３６内に配されたポンプロータ３２は駆動軸２８とともに回転する。一連のスライド式ポンプ羽根４０はロータ３２とともに回転し、各々の羽根４０の外端は、チャンバ３６の外壁を形成するポンプ制御リング４４の内周面に接合している。ポンプチャンバ３６は、ポンプ制御リング４４の内周面とポンプロータ３２と羽根４０とによって画定される一連の作動流体チャンバ４８に区分される。ポンプロータ３２は、ポンプ制御リング４４の中心から偏心した回転軸を有している。   The pump 20 includes a drive shaft 28 that is driven by any suitable means, such as an engine or other mechanism to which the pump supplies working fluid, to operate the pump 20. When the drive shaft 28 is rotated, the pump rotor 32 disposed in the pump chamber 36 rotates together with the drive shaft 28. A series of sliding pump blades 40 rotate with the rotor 32, and the outer end of each blade 40 is joined to the inner peripheral surface of the pump control ring 44 that forms the outer wall of the chamber 36. The pump chamber 36 is divided into a series of working fluid chambers 48 defined by the inner peripheral surface of the pump control ring 44, the pump rotor 32 and the vanes 40. The pump rotor 32 has a rotation shaft that is eccentric from the center of the pump control ring 44.

ポンプ制御リング４４は、ポンプ制御リング４４の中心がロータ３２の中心に対して相対運動することを可能にする軸ピン５２を介してケーシング２２内に取付けられている。ポンプ制御リング４４の中心はポンプロータ３２の中心に対して偏心配置され、かつポンプ制御リング４４とポンプロータ３２とのそれぞれの内周は円形であることから、作動流体チャンバ４８の容積はチャンバ４８がポンプチャンバ３６を周回するにつれて変化し、それらの容積はポンプ２０の低圧側（図１においてポンプチャンバ３６の左側）で大きくなり、ポンプ２０の高圧側（図１においてポンプチャンバ３６の右側）で小さくなる。作動流体チャンバ４８のこの容積変化がポンプ２０のポンプ作用を生み出して、吸込み口５０から作動流体を吸込んで加圧し、吐出し口５４に送達する。   The pump control ring 44 is mounted in the casing 22 via a shaft pin 52 that allows the center of the pump control ring 44 to move relative to the center of the rotor 32. Since the center of the pump control ring 44 is eccentrically arranged with respect to the center of the pump rotor 32 and the inner periphery of each of the pump control ring 44 and the pump rotor 32 is circular, the volume of the working fluid chamber 48 is the chamber 48. Change as they circulate around the pump chamber 36 and their volumes increase on the low pressure side of the pump 20 (left side of the pump chamber 36 in FIG. 1) and on the high pressure side of the pump 20 (right side of the pump chamber 36 in FIG. 1). Get smaller. This change in volume of the working fluid chamber 48 creates the pumping action of the pump 20, sucking and pressurizing working fluid from the suction port 50 and delivering it to the discharge port 54.

ポンプ制御リング４４を軸ピン５２周りに旋回運動させることでポンプロータ３２に対する偏心量を変化させて、ポンプ２０の低圧側からポンプ２０の高圧側に向かって変化する作動流体チャンバ４８の容積量を変えることができ、従って、ポンプ容積を変化させることができる。戻しばね５６は、ポンプが最大偏心量を有する、図１および２に示した位置に向かってポンプ制御リング４４を付勢している。   By rotating the pump control ring 44 around the shaft pin 52, the amount of eccentricity with respect to the pump rotor 32 is changed, and the volume of the working fluid chamber 48 that changes from the low pressure side of the pump 20 toward the high pressure side of the pump 20 is changed. The pump volume can be changed. The return spring 56 biases the pump control ring 44 toward the position shown in FIGS. 1 and 2 where the pump has the maximum amount of eccentricity.

上述したように、ポンプリングに隣接して制御チャンバと戻しばねとを設けて、可変容量形ベーンポンプのポンプリングを運動させ、平衡吐出し量、およびこれに関する平衡圧力とを実現することは公知に属する。   As mentioned above, it is well known to provide a control chamber and return spring adjacent to the pump ring to move the pump ring of the variable displacement vane pump to achieve an equilibrium discharge rate and an equilibrium pressure associated therewith. Belongs.

ただし、本発明によれば、ポンプ２０は、図３から最もよく看取し得るように、ポンプリング４４を制御する２つの制御チャンバ６０と６４とを含んでいる。制御チャンバ６０つまり図３において右側の斜め線の付された部分は、ポンプケーシング２２と、ポンプ制御リング４４と、軸ピン５２と、ポンプ制御リング４４およびそれに当接するケーシング２２に取り付けられた弾性シール６８との間に形成されている。図示した実施形態において、ポンプ吐出し口５４に供給されるポンプ２０からの加圧作動流体が制御チャンバ６０も充填するように、制御チャンバ６０はポンプ吐出し口５４と直接に流体連通している。   However, according to the present invention, the pump 20 includes two control chambers 60 and 64 that control the pump ring 44 as best seen in FIG. The control chamber 60, that is, the hatched portion on the right side in FIG. 3, is an elastic seal attached to the pump casing 22, the pump control ring 44, the shaft pin 52, the pump control ring 44 and the casing 22 abutting on the pump control ring 44. 68. In the illustrated embodiment, the control chamber 60 is in direct fluid communication with the pump outlet 54 such that the pressurized working fluid from the pump 20 supplied to the pump outlet 54 also fills the control chamber 60. .

当業者には明らかなように、制御チャンバ６０はポンプ吐出し口５４と直接に流体連通している必要はなく、それに代えて、任意の適切な作動流体源例えばポンプ２０によって供給される自動車エンジンのオイルギャラリから供給されてよい。   As will be apparent to those skilled in the art, the control chamber 60 need not be in direct fluid communication with the pump outlet 54, but instead is an automotive engine supplied by any suitable source of working fluid, such as the pump 20. From the oil gallery.

制御チャンバ６０内の加圧作動流体はポンプ制御リング４４に作用して、加圧作動流体の圧力から生ずるポンプ制御リング４４に作用する力が戻しばね５６の付勢力を克服するのに十分であれば、ポンプ制御リング４４を軸ピン５２周りに、図３の矢印７２によって示されている方向に旋回させ、ポンプ２０の偏心量を減少させる。加圧作動流体の圧力が戻しばね５６の付勢力を克服するのに十分でなければ、ポンプ制御リング４４は軸ピン５２周りに、矢印７２によって示されているのとは反対の方向に旋回して、ポンプ２０の偏心量を増大させる。   The pressurized working fluid in the control chamber 60 acts on the pump control ring 44 so that the force acting on the pump control ring 44 resulting from the pressure of the pressurized working fluid is sufficient to overcome the biasing force of the return spring 56. For example, the pump control ring 44 is pivoted around the shaft pin 52 in the direction indicated by the arrow 72 in FIG. 3 to reduce the amount of eccentricity of the pump 20. If the pressure of the pressurized working fluid is not sufficient to overcome the biasing force of the return spring 56, the pump control ring 44 pivots about the shaft pin 52 in the opposite direction as indicated by the arrow 72. Thus, the eccentric amount of the pump 20 is increased.

ポンプ２０はさらに第２の制御チャンバ６４、つまり図３において左端の斜め線の付された部分を含んでおり、これはポンプケーシング２２と、ポンプ制御リング４４と、弾性シール６８と、第２の弾性シール７６と、の間に形成されている。弾性シール７６は、ポンプケーシング２２の壁面に当接して制御チャンバ６４をポンプ吸込み口５０から分離し、弾性シール６８はチャンバ６４をチャンバ６０から分離している。   The pump 20 further includes a second control chamber 64, i.e., the leftmost hatched portion in FIG. 3, which includes a pump casing 22, a pump control ring 44, a resilient seal 68, a second seal. And an elastic seal 76. The elastic seal 76 contacts the wall surface of the pump casing 22 to separate the control chamber 64 from the pump suction port 50, and the elastic seal 68 separates the chamber 64 from the chamber 60.

制御チャンバ６４には、制御孔８０を通じて加圧作動流体が供給される。制御孔８０には、ポンプ吐出し口５４、またはエンジン内の作動流体ギャラリ、またはポンプ２０から供給されるその他の装置を含む任意の適切な流体源から加圧作動流体が供給されてよい。以下に述べるように、制御孔８０を通じてチャンバ６４に作動流体を選択的に供給するために、制御機構（図示せず）、例えばソレノイド作動弁または切換え弁機構が採用される。制御チャンバ６０の場合と同様に、制御孔８０から制御チャンバ６４に供給された加圧作動流体もポンプ制御リング４４に作用する。   A pressurized working fluid is supplied to the control chamber 64 through the control hole 80. Control hole 80 may be supplied with pressurized working fluid from any suitable fluid source, including pump outlet 54, or a working fluid gallery in the engine, or other device fed from pump 20. As described below, a control mechanism (not shown), such as a solenoid operated valve or a switching valve mechanism, is employed to selectively supply working fluid to the chamber 64 through the control hole 80. As in the case of the control chamber 60, the pressurized working fluid supplied from the control hole 80 to the control chamber 64 also acts on the pump control ring 44.

ここで判明するように、ポンプ吐出し口５４に供給される加圧作動流体は制御チャンバ６０も満たすことから、ポンプ２０は従来のように作動して平衡圧力を達成することができる。作動流体の圧力が平衡圧力よりも大きければ、供給された作動流体の圧力によってチャンバ６０内に存在するポンプ制御リング４４の部分に生み出された力は、戻しばね５６の力に打ち勝ってポンプ制御リング４４を可動させ、ポンプ２０の容積を減少させる。逆に、作動流体の圧力が平衡圧力よりも小さければ、戻しばね５６の力は、供給された作動流体の圧力によってチャンバ６０内に存在するポンプ制御リング４４の部分に生み出された力を上回り、戻しばね５６がポンプリング４４を旋回運動させて、ポンプ２０の容積を増大させることになる。   As can be seen, the pressurized working fluid supplied to the pump outlet 54 also fills the control chamber 60 so that the pump 20 can operate in the conventional manner to achieve an equilibrium pressure. If the working fluid pressure is greater than the equilibrium pressure, the force generated in the portion of the pump control ring 44 present in the chamber 60 by the pressure of the supplied working fluid overcomes the force of the return spring 56 and the pump control ring. 44 is moved to reduce the volume of the pump 20. Conversely, if the pressure of the working fluid is less than the equilibrium pressure, the force of the return spring 56 will exceed the force created in the portion of the pump control ring 44 present in the chamber 60 by the pressure of the supplied working fluid, The return spring 56 causes the pump ring 44 to pivot and increase the volume of the pump 20.

ただし、従来のポンプとは異なり、ポンプ２０は第２の平衡圧力で作動することが可能である。とりわけ、制御孔８０を経て制御チャンバ６４に加圧作動流体を選択的に供給することにより、第２の平衡圧力を選択することができる。例えば、エンジン制御系によって制御されるソレノイド作動弁は制御孔８０を経て制御チャンバ６４に加圧作動流体を供給して、加圧作動流体によってポンプ制御リング４４のチャンバ６４内の該当部分に生み出された力が制御チャンバ６０内の加圧作動流体によって生み出された力に加えられ、これにより、ポンプ制御リング４４をそうでない場合よりもさらに旋回運動させて、ポンプ２０にとって新しい、より低い平衡圧力を達成することができる。   However, unlike conventional pumps, the pump 20 can operate at a second equilibrium pressure. In particular, the second equilibrium pressure can be selected by selectively supplying a pressurized working fluid to the control chamber 64 via the control hole 80. For example, a solenoid actuated valve controlled by the engine control system supplies pressurized working fluid to the control chamber 64 via the control hole 80 and is created by the pressurized working fluid in the relevant part of the chamber 64 of the pump control ring 44. Force is added to the force generated by the pressurized working fluid in the control chamber 60, which causes the pump control ring 44 to pivot further than otherwise, creating a new, lower equilibrium pressure for the pump 20. Can be achieved.

一例として、ポンプ２０の低速作動速度で、加圧作動流体は双方のチャンバ６０、６４に供給されればよく、ポンプリング４４は、該ポンプリングを該ポンプ容積が低速の作動速度で受け入れ可能な第１の、より低い平衡圧力を生み出す位置に可動させることができる。   As an example, at the slow operating speed of the pump 20, pressurized working fluid need only be supplied to both chambers 60, 64, and the pump ring 44 can accept the pump ring at an operating speed at which the pump volume is slow. The first can be moved to a position that produces a lower equilibrium pressure.

ポンプ２０がより高速で駆動される場合には、制御機構が作動して制御チャンバ６４への加圧作動流体の供給を排除し、これにより、戻しばね５６によりポンプリング４４を可動させてポンプ２０にとって第２の平衡圧力を達成することができる。この第２の平衡圧力は第１の平衡圧力よりも高い。   When the pump 20 is driven at a higher speed, the control mechanism is activated to eliminate the supply of pressurized working fluid to the control chamber 64, thereby moving the pump ring 44 by the return spring 56 and moving the pump 20. A second equilibrium pressure can be achieved. This second equilibrium pressure is higher than the first equilibrium pressure.

図示した実施形態においてチャンバ６０はポンプ吐出し口５４と流体連通しているが、所望であれば、制御チャンバ６０の設計を変更して、該チャンバに加圧作動流体が、ポンプ吐出し口５４ではなく制御孔８０と同様な制御孔から供給されるようにすることが当業者にとって容易であることは明らかであろう。こうした場合には、制御機構（図示せず）例えばソレノイド作動弁または切換え弁機構を採用して、該制御孔を通じて制御チャンバ６０に作動流体を選択的に供給することができる。それぞれの制御チャンバ６０および６４内に存在する制御リング４４の部分の面積は相違していることから、制御チャンバ６０または制御チャンバ６４または制御チャンバ６０，６４の双方に加圧作動流体を選択的に付与することにより、所望通り、３つの異なった平衡圧力を達成することが可能である。   In the illustrated embodiment, the chamber 60 is in fluid communication with the pump outlet 54, but if desired, the design of the control chamber 60 can be modified to allow pressurized working fluid to be pumped into the pump outlet 54. It will be apparent to those skilled in the art that it can be supplied from a control hole similar to control hole 80 rather than from. In such a case, a control mechanism (not shown) such as a solenoid operated valve or a switching valve mechanism may be employed to selectively supply the working fluid to the control chamber 60 through the control hole. Since the areas of the portions of the control ring 44 present in the respective control chambers 60 and 64 are different, the pressurized working fluid is selectively applied to the control chamber 60 or the control chamber 64 or both of the control chambers 60 and 64. By applying, it is possible to achieve three different equilibrium pressures as desired.

さらにまた当業者にとって明らかなように、もし追加的な平衡圧力が所望されるならば、ポンプケーシング２２と制御リング４４とを、必要に応じて１つまたは複数の追加的な制御チャンバが形成されるように製造することも可能である。   Furthermore, as will be apparent to those skilled in the art, if additional equilibrium pressure is desired, the pump casing 22 and control ring 44 may be formed, optionally with one or more additional control chambers. It is also possible to manufacture as follows.

ポンプ２０は、従来のベーンポンプ例えば図４に示したポンプ２００と比較してさらなる利点を供する。従来のベーンポンプ例えばポンプ２００において、ポンプチャンバ内の低圧流体２０４は、ポンプチャンバ内の高圧流体２０８と同様にポンプリング２１６に力を及ぼす。これらの力はポンプ制御リング２１６に作用する有効力２１２を生じさせ、この力のほとんどは、力２１２が作用する点に配置される軸ピン２２０によって担われる。   The pump 20 provides further advantages compared to a conventional vane pump, such as the pump 200 shown in FIG. In a conventional vane pump, such as pump 200, low pressure fluid 204 in the pump chamber exerts a force on pump ring 216, similar to high pressure fluid 208 in the pump chamber. These forces produce an effective force 212 acting on the pump control ring 216, most of which is carried by the shaft pin 220 located at the point where the force 212 acts.

さらにまた、吐出し口２２４（鎖線によって表示）内の高圧流体は、ポンプリング２１６の軸ピン２２０と弾性シール２２２との間の部分全体に作用して、ポンプ制御リング２１６に作用する有効力２２８も生ずる。力２２８は戻しばね２３６の力２３２によってある程度相殺されるとはいえ、力２３２によって相殺された後の力２２８の正味の力はなお有効であり、この正味の力もそのほとんどが軸ピン２２０によって担われる。   Furthermore, the high-pressure fluid in the discharge port 224 (indicated by a chain line) acts on the entire portion between the shaft pin 220 and the elastic seal 222 of the pump ring 216, and an effective force 228 acting on the pump control ring 216. Also occurs. Although the force 228 is offset to some extent by the force 232 of the return spring 236, the net force 228 after it is canceled by the force 232 is still effective, and most of this net force is also carried by the shaft pin 220. Is called.

こうして軸ピン２２０は有効力２１２と２２８とにそれぞれ対抗して、大きな反力２４０と２４４とを担うこととなり、これらの力は時と共に軸ピン２２０の望ましくない摩耗および／またはポンプ制御リング２１６の「静止摩擦力」を生じ、その結果、該リングは軸ピン２２０周りに円滑に旋回せず、ポンプ２００の精密制御の達成はより困難になる。   The shaft pin 220 thus bears large reaction forces 240 and 244 against the effective forces 212 and 228, respectively, which over time can cause undesirable wear of the shaft pin 220 and / or the pump control ring 216. A “static frictional force” is created, so that the ring does not pivot smoothly around the shaft pin 220, making it more difficult to achieve precise control of the pump 200.

図５に示したように、ポンプ２０の低圧側３００と高圧側３０４とは、軸ピン５２のほぼ直上でポンプ制御リング４４に作用する有効力３０８を生ずるとともに、（図中に示した向きにおいて）水平力３１２として示した、軸ピン５２に作用する対応する反力が生み出される。従来の可変容量形ベーンポンプ例えばポンプ２００とは異なり、ポンプ２０において弾性シール６８は、制御チャンバ６０内の加圧作動流体が作用するポンプ制御リング４４の部分の面積が減少するように軸ピン５２に比較的近接して配置されており、従ってポンプ制御リング４４に作用する力３１６の大きさも有意に減少する。   As shown in FIG. 5, the low pressure side 300 and the high pressure side 304 of the pump 20 generate an effective force 308 that acts on the pump control ring 44 almost directly above the shaft pin 52 (in the orientation shown in the figure). ) A corresponding reaction force acting on the shaft pin 52, shown as a horizontal force 312 is produced. Unlike conventional variable displacement vane pumps, such as pump 200, in pump 20, elastic seal 68 is attached to shaft pin 52 to reduce the area of the portion of pump control ring 44 where pressurized working fluid in control chamber 60 acts. The magnitude of the force 316 acting on the pump control ring 44 is also significantly reduced because of its relatively close proximity.

さらに、制御チャンバ６０は、力３１６が力３０８に対抗して作用する水平成分を含むように配置されており、従って、軸ピン５２に生ずる反力３１２は減少する。力３１６の（図中に示した向きにおいて）垂直成分は軸ピン５２に作用する垂直反力３２０を生じはするが、上述したように、力３１６の大きさは従来のポンプの場合に考えられるよりも小さく、また垂直反力３２０は戻しばね５６によって生み出される付勢力３２４の垂直成分によっても減少させられる。   In addition, the control chamber 60 is arranged such that the force 316 includes a horizontal component that acts against the force 308, thus reducing the reaction force 312 generated on the shaft pin 52. Although the vertical component of force 316 (in the orientation shown in the figure) produces a vertical reaction force 320 acting on the shaft pin 52, as described above, the magnitude of the force 316 is considered in the case of a conventional pump. The vertical reaction force 320 is also reduced by the vertical component of the biasing force 324 produced by the return spring 56.

こうして、制御チャンバ６０と戻しばね５６との軸ピン５２に対する固有な配置によって、軸ピン５２に作用する反力を減少させ、ポンプ２０の作動耐用年数を向上させるとともに、制御リング４４の「静止摩擦力」を減少させてポンプ２０のより円滑な制御が可能になる。当業者には明らかなように、この固有な配置は２つまたはそれ以上の平衡圧力が達成される可変容量形ベーンポンプに制限されるものではなく、単一の平衡圧力で作動する可変容量形ベーンポンプに採用することも可能である。   In this way, the unique arrangement of the control chamber 60 and the return spring 56 with respect to the shaft pin 52 reduces the reaction force acting on the shaft pin 52, improves the service life of the pump 20, and improves the "static friction" of the control ring 44. The “force” is reduced, and the pump 20 can be controlled more smoothly. As will be apparent to those skilled in the art, this unique arrangement is not limited to variable displacement vane pumps in which two or more equilibrium pressures are achieved, but variable displacement vane pumps that operate at a single equilibrium pressure. It is also possible to adopt it.

本発明の上述した実施形態は本発明の例示を目的としたものであり、本願明細書に添付の請求項によってもっぱら画定される本発明の範囲を逸脱することなく、当業者による改変および変形が行なわれてよい。   The above-described embodiments of the present invention are intended to be exemplary of the present invention, and modifications and variations by those skilled in the art can be made without departing from the scope of the present invention, which is defined solely by the claims appended hereto. May be performed.

ロータ偏心率が最大となるように配置された制御リングを備えた本発明に係る可変容量形ベーンポンプの正面図である。It is a front view of the variable displacement type vane pump concerning the present invention provided with the control ring arranged so that rotor eccentricity may become the maximum. ロータ偏心率が最大となるように配置された制御リングを備えた図１のポンプの正面斜視図である。FIG. 2 is a front perspective view of the pump of FIG. 1 with a control ring arranged to maximize the rotor eccentricity. 偏心率が最小となるように位置された制御リングを備えた図１のポンプの正面図であり、ポンプ制御チャンバの部分は斜め線で表されている。FIG. 2 is a front view of the pump of FIG. 1 with a control ring positioned to minimize eccentricity, with portions of the pump control chamber represented by diagonal lines. 従来技術の可変容量形ポンプの概略図である。It is the schematic of the variable displacement pump of a prior art. 図１のポンプの正面図であり、ロータとベーンは、ポンプ内部の力を具体的に示すために取り除かれている。FIG. 2 is a front view of the pump of FIG. 1 with the rotor and vanes removed to illustrate the force inside the pump.

Claims (10)

ポンプ容量を変化させる可動式ポンプ制御リングを備え、選択された少なくとも２つの平衡圧力で作動可能な可変容量形ベーンポンプであって、
吸込み口と吐出し口とを有するポンプチャンバを内蔵したポンプケーシングと、
前記ポンプチャンバ内を可動して前記ポンプの容量を変化させるポンプ制御リングと、
前記ポンプ制御リング内に回転式に取り付けられたベーンポンプロータであって、前記ポンプ制御リングの内周面に接合するスライド式に取り付けられた複数枚の羽根を有し、前記ポンプ制御リングの中心から偏心した回転軸を有し、回転して、流体が前記吸込み口から前記吐出し口に向かって移動するにつれて流体を加圧するベーンポンプロータと、
前記ポンプケーシングと前記ポンプ制御リングとの間にある第１の制御チャンバであって、加圧流体を受け取って、前記ポンプの容積を減少させるために前記ポンプ制御リングを可動させる力を生み出すように作動する第１の制御チャンバと、
前記ポンプケーシングと前記ポンプ制御リングとの間にある第２の制御チャンバであって、加圧流体を受け取って、前記ポンプの容積を減少させるために前記ポンプ制御リングを可動させる力を生み出すように選択的に作動する第２の制御チャンバと、
前記ポンプリングと前記ケーシングとの間で作用して、最大容積が達成される位置に向かって前記ポンプリングを付勢する戻しばねであって、前記第１と第２の制御チャンバの力に抗して作用して平衡圧力を達成する戻しばねと、を備え、
前記第２の制御チャンバに対する加圧流体の供給を実施もしくは排除させることによって前記ポンプの前記平衡圧力が変化させられる、可変容量形ベーンポンプ。 A variable displacement vane pump with a movable pump control ring that varies the pump capacity and is operable at at least two selected equilibrium pressures;
A pump casing incorporating a pump chamber having a suction port and a discharge port;
A pump control ring that moves within the pump chamber to change the capacity of the pump;
A vane pump rotor that is rotatably mounted in the pump control ring, and includes a plurality of blades that are slidably attached to an inner peripheral surface of the pump control ring, from the center of the pump control ring A vane pump rotor having an eccentric rotation shaft, rotating, and pressurizing the fluid as the fluid moves from the suction port toward the discharge port;
A first control chamber between the pump casing and the pump control ring for receiving pressurized fluid and generating a force to move the pump control ring to reduce the volume of the pump A first control chamber that operates;
A second control chamber between the pump casing and the pump control ring for receiving pressurized fluid and generating a force to move the pump control ring to reduce the volume of the pump A second control chamber that operates selectively;
A return spring acting between the pump ring and the casing to urge the pump ring toward a position where maximum volume is achieved, resisting the forces of the first and second control chambers A return spring that acts to achieve an equilibrium pressure,
A variable displacement vane pump wherein the equilibrium pressure of the pump is varied by implementing or eliminating the supply of pressurized fluid to the second control chamber. 加圧流体が前記ポンプ作動時に前記第１の制御チャンバに供給され、また加圧流体は制御系からの信号に応じてのみ第２の制御チャンバに供給される、請求項１記載の可変容量形ポンプ。   The variable displacement type of claim 1, wherein pressurized fluid is supplied to the first control chamber when the pump is activated, and pressurized fluid is supplied to the second control chamber only in response to a signal from a control system. pump. 前記第２の制御チャンバには制御孔から加圧流体が供給される、請求項１記載の可変容量形ポンプ。   The variable displacement pump according to claim 1, wherein pressurized fluid is supplied to the second control chamber from a control hole. 前記第１の制御チャンバは前記吐出し口と流体連通し、前記吐出し口から加圧流体を受け取る、請求項１記載の可変容量形ポンプ。   The variable displacement pump of claim 1, wherein the first control chamber is in fluid communication with the outlet and receives pressurized fluid from the outlet. 前記第２の制御チャンバは、前記ポンプケーシングと、前記ポンプ制御リングと、前記ポンプ制御リングと前記ポンプケーシングとの間で作用する第１および第２の弾性シールとによって形成される、請求項１記載の可変容量形ポンプ。   The second control chamber is formed by the pump casing, the pump control ring, and first and second elastic seals acting between the pump control ring and the pump casing. The variable displacement pump as described. 加圧流体の供給は、前記第１および第２の制御チャンバのいずれか一方または双方に行われて、前記ポンプの３つの平衡圧力からいずれか１つが選択し得る、請求項１記載の可変容量形ポンプ。   The variable capacity according to claim 1, wherein supply of pressurized fluid is performed to one or both of the first and second control chambers, and any one of the three equilibrium pressures of the pump can be selected. Shape pump. 加圧流体を受け取って、前記ポンプの容積を減少させるために前記ポンプ制御リングを可動させる力を生み出すように作動可能な第３の制御チャンバをさらに備えた、請求項１記載の可変容量形ポンプ。   The variable displacement pump of claim 1, further comprising a third control chamber operable to receive pressurized fluid and generate a force to move the pump control ring to reduce the volume of the pump. . ポンプチャンバを内蔵したポンプケーシングと、
前記ポンプチャンバ内に回転式に取り付けられたベーンポンプロータと、
前記ベーンポンプロータにスライド式に取り付けられた複数の羽根と、
前記ポンプチャンバ内で前記ベーンポンプロータを包囲するポンプ制御リングであって、前記ベーンポンプロータは前記ポンプ制御リングの中心から偏心した回転軸を有し、前記ポンプ制御リングは前記ポンプの容量を変化させるために、前記ポンプチャンバ内で軸ピン周りに旋回運動可能なポンプ制御リングと、
前記ポンプケーシングと、前記ポンプ制御リングと、前記軸ピンと、前記ポンプ制御リングおよび前記ポンプケーシングの間の弾性シールと、の間に形成された制御チャンバであって、加圧流体を受け取って、前記ポンプの容積を減少させるために前記ポンプ制御リングを可動させる力を生み出すように作動可能な制御チャンバと、
ポンプリングと前記ケーシングとの間で作用して、最大容積が達成される位置に向かって前記ポンプリングを付勢する戻しばねであって、前記戻しばねは、前記制御チャンバの力に抗して作用して平衡圧力を達成し、前記軸ピンおよび前記弾性シールは、前記制御チャンバ内に存在する前記ポンプ制御リングの面積が減少するように配置され、前記制御チャンバ内の加圧流体によって前記ポンプ制御リングに及ぼされる力を減少させる、可変容量形ベーンポンプ。 A pump casing with a built-in pump chamber;
A vane pump rotor mounted rotatably in the pump chamber;
A plurality of blades slidably attached to the vane pump rotor;
A pump control ring surrounding the vane pump rotor in the pump chamber, the vane pump rotor having a rotating shaft eccentric from a center of the pump control ring, the pump control ring for changing a capacity of the pump And a pump control ring capable of swiveling around an axial pin within the pump chamber;
A control chamber formed between the pump casing, the pump control ring, the shaft pin, and an elastic seal between the pump control ring and the pump casing, receiving pressurized fluid, A control chamber operable to produce a force to move the pump control ring to reduce the volume of the pump;
A return spring acting between the pump ring and the casing to bias the pump ring toward a position where maximum volume is achieved, the return spring resisting the force of the control chamber Acting to achieve an equilibrium pressure, wherein the shaft pin and the elastic seal are arranged to reduce the area of the pump control ring present in the control chamber, and the pump fluid by the pressurized fluid in the control chamber Variable displacement vane pump that reduces the force exerted on the control ring. 前記戻しばねは、前記戻しばねが前記ポンプ制御リングに加える付勢力が前記軸ピンに作用する反力をさらに減少させる方向を指向する、請求項８記載の可変容量形ベーンポンプ。   9. The variable displacement vane pump according to claim 8, wherein the return spring is directed in a direction in which a biasing force applied to the pump control ring by the return spring further reduces a reaction force acting on the shaft pin. 前記制御チャンバは、前記軸ピンに対して、生ずる力が前記軸ピンに作用する反力を減少させるように配置される、請求項８記載の可変容量形ベーンポンプ。   The variable displacement vane pump according to claim 8, wherein the control chamber is arranged to reduce a reaction force applied to the shaft pin by the generated force with respect to the shaft pin.
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